EP0631053B1 - Wave plate type compressor - Google Patents

Wave plate type compressor Download PDF

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Publication number
EP0631053B1
EP0631053B1 EP94108724A EP94108724A EP0631053B1 EP 0631053 B1 EP0631053 B1 EP 0631053B1 EP 94108724 A EP94108724 A EP 94108724A EP 94108724 A EP94108724 A EP 94108724A EP 0631053 B1 EP0631053 B1 EP 0631053B1
Authority
EP
European Patent Office
Prior art keywords
portions
piston
cam
axis
rotary shaft
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP94108724A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0631053A1 (en
Inventor
Kazuo C/O K.K. Toyoda Murakami
Kunifumi C/O K.K. Toyoda Goto
Masahiro C/O K.K. Toyoda Kawaguchi
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Toyota Industries Corp
Original Assignee
Toyoda Jidoshokki Seisakusho KK
Toyoda Automatic Loom Works Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Toyoda Jidoshokki Seisakusho KK, Toyoda Automatic Loom Works Ltd filed Critical Toyoda Jidoshokki Seisakusho KK
Publication of EP0631053A1 publication Critical patent/EP0631053A1/en
Application granted granted Critical
Publication of EP0631053B1 publication Critical patent/EP0631053B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B25/00—Multi-stage pumps
    • F04B25/04—Multi-stage pumps having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B1/141—Details or component parts
    • F04B1/146—Swash plates; Actuating elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1054—Actuating elements
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18056—Rotary to or from reciprocating or oscillating
    • Y10T74/18296—Cam and slide
    • Y10T74/18336—Wabbler type

Definitions

  • the present invention relates to a wave plate type compressor in which a piston reciprocates in response to the rotation of a wave plate secured to a rotary shaft.
  • one head of a double-headed piston completes a single compression cycle for every rotation made by the swash plate and the rotary shaft.
  • one head of the double-headed piston completes a plurality of compression cycles in accordance with the shapes of the cam surfaces or cam grooves on the wave plate for each rotation of the rotary shaft.
  • the wave plate type compressors therefore have an advantage over the swash plate type compressor in that the discharge displacement per rotation is increased.
  • rollers 53 and 54 are provided between an associated double-headed piston 52 and the front and rear cam surfaces 5la and 51b of a wave plate 51 as shown in Fig. 13.
  • the rollers 53 and 54 are rotatably fitted in the piston 52, and are capable of rolling on the wave plate 51.
  • the wave plate 51 rotates, its cam surfaces 51a and 51b engage and displace the rollers 53 and 54. These rollers then transmit this displacement to the piston 52, in turn, causing its reciprocation.
  • cam grooves are formed on the front and rear surfaces of the wave plate instead of the cam surfaces.
  • balls rather than rollers are interposed between the cam groove and double-headed piston.
  • rollers or balls may at first appear to be in line contact with the wave plate, a microscopic view reveals a plane contact exists between the contacting components due to their deformation under pressure. This deformation results in the occurrence of the so called "Hertz contact which effectively increases the contact area shared between the rollers or balls and the wave plate.
  • the compressor has a plate rotatable about an axis of a rotary shaft and a piston connected to the plate.
  • the plate causes the piston to reciprocate between a top dead center and a bottom dead center in accordance with the rotation movement of the plate.
  • Cam means is provided with the plate for actuating the piston.
  • the cam means has first portions for driving the piston toward the top dead center, and second portions for driving the piston toward the bottom dead center.
  • Transmission means is interposed between the piston and the plate for transmitting the rotation movement of the plate to the piston.
  • the first and second portions cause the transmission means to displace on the cam means.
  • At least one of the first and second portions are arranged to have a normal line extending obliquely to the axis of the rotary shaft for a constant contact between the transmission means and the one of the portions.
  • a rotary shaft 3 is rotatable supported via bearings 4 and 5 in a pair of cylinder blocks 1 and 2 which are secured to each other.
  • a plurality of bores 1a and 2a (five each in this embodiment) are respectively formed in the cylinder blocks 1 and 2 at equiangular distances on a plurality of axes L1 located on an imaginary circumferential plane C0 around the axis, L0, of the rotary shaft 3.
  • Each bore 1a in the front cylinder block 1 is paired with the associated bore 2a in the cylinder block 2, thereby forming a plurality of cylinder bores.
  • a plurality of double-headed pistons 6 are reciprocally retained in the respective bores 1a and 2a.
  • a wave plate 7, secured to the rotary shaft 3, has cam surfaces 7a and 7b formed with a predetermined width at the front and rear portions of the wave plate 7.
  • a pair of shoes 8 and 9 are provided between the wave plate 7 and each piston 6.
  • the piston 6 has a pair of recesses 6a and 6b at the center.
  • the shoes 8 and 9 have first spherical surfaces 8a and 9b, which are fitted in the respective recesses 6a and 6b, and second spherical surfaces 8b and 9b, which slide on the respective cam surfaces 7a and 7b of the wave plate 7.
  • the radius of curvature R1 of the second spherical surfaces 8b and 9b is larger than the radius of curvature R2 of the first spherical surfaces 8a and 9a.
  • the centers, Q1 and Q2, of the first spherical surfaces 8a and 9a are located substantially at the centers of the second spherical surfaces 8b and 9b.
  • the cam surfaces 7a and 7b of the wave plate 7 are located on a displacement curve F on the circumferential surface C0.
  • the displacement curve F is a 2-cycle displacement curve which has four first portions alternately protruding forward and rearward (leftward and rightward in Fig. 1) with respect to a plane perpendicular to the axis L0 of the rotary shaft 3. In addition, second portions are provided that link the four first portions. Examples of the displacement curve F of the cam surfaces 7a and 7b include a sinusoidal displacement curve and a cycloid displacement curve.
  • the piston 6 reciprocates twice.
  • the reciprocation of the piston 6 causes the refrigerant gas in a suction chamber 10 to enter the bores 1a and 2a via inlet ports 12 and associated inlet valves 11.
  • the refrigerant gas in the bores 1a and 2a is exhausted to a discharge chamber 15 via discharge ports 14 and associated discharge valves 13.
  • the cam surfaces 7a and 7b have cross sections on a plane containing the axis L0 along an arc, which has the same radius of curvature as the radius of curvature R1 of the second spherical surfaces 8b and 9b. Therefore, the second spherical surfaces 8b and 9b of the shoes 8 and 9 have a line contact with the cam surfaces 7a and 7b. Since the centers Q1 and Q2 of the first spherical surfaces 8a and 9a are located at the centers of the second spherical surfaces 8b and 9b, the displacement of the piston 6 accurately reflects the displacement of the cam surfaces 7a and 7b on the displacement curve F of the cam 7.
  • Fig. 4 illustrates the wave plate 7 turned 90 degrees from the position in Fig. 3.
  • a pair of rightmost portions 7a1 of the front cam surface 7a are arranged at an angular distance of 180 degrees from each other.
  • a pair of leftmost portions 7a2 are respectively separated from the pair of rightmost portions 7a1 by 90 degrees.
  • a leftmost portion 7b1 of the rear cam surface 7b is located at the back of the leftmost portion 7a2 of the front cam surface 7a.
  • a rightmost portion 7b2 of the rear cam surface 7b is located at the rear of the rightmost portion 7a1 of the front cam surface 7a.
  • the rightmost portion 7a1 of the cam surface 7a is used for driving the piston 6 toward the bottom dead center on the side of the bore 1a.
  • the leftmost portion 7a2 of the cam surface 7a is used for driving the piston 6 toward the top dead center on the side of the bore 1a.
  • the leftmost portion 7b1 of the cam surface 7b is used for driving the piston 6 toward the bottom dead center of the piston 6 on the side of the bore 2a.
  • the rightmost portion 7b2 of the cam surface 7b is used for driving the piston 6 toward the top dead center of the piston 6 on the side of the bore 2a.
  • the leftmost portion 7a2 (corresponding to the top dead center) of the cam surface 7a is located on a circle Ca2 indicated by a chain line in Fig. 3.
  • the leftmost portion 7b1 (corresponding to the bottom dead center) of the cam surface 7b is located on a circle Cb1 and to also indicated by a chain line in Fig 3.
  • the rightmost portion 7a1 (corresponding to the bottom dead center) of the cam surface 7a is located on a circle Ca1 as indicated by a chain line in Fig. 4.
  • the rightmost portion 7b2 (corresponding to the top dead center) of the cam surface 7b is located on a circle Cb2 and is similarly indicated by a chain line in Fig. 4.
  • the circles Ca1, Ca2, Cb1 and Cb2 have the same radius.
  • a normal vector Va1 on the displacement curve F at the rightmost portion 7a1 (the bottom-dead-center portion, hereinafter referred to BDC portion) of the cam surface 7a is inclined outward with respect to the axis L0 of the rotary shaft 3.
  • a normal vector Va2 on the displacement curve F at the leftmost portion 7a2 (the top-dead-center portion, hereinafter referred to TDC portion) of the cam surface 7a is parallel to the axis L0 of the rotary shaft 3.
  • a normal vector Vb1 on the cycle displacement curve F at the leftmost portion 7b1 (the BDC portion) of the cam surface 7b is inclined outward with respect to the axis L0 of the rotary shaft 3.
  • a normal vector Vb2 on the displacement curve F at the rightmost portion 7b2 (the TDC portion) of the cam surface 7b is parallel to the axis L0 of the rotary shaft 3.
  • a normal vector on the displacement curve F of the cam surface 7a is gradually inclined outward, with respect to the axis L0 between the TDC portion 7a2 and the BDC portion 7a1 as the normal vector position is shifted toward the BDC portion 7a1 from the TDC portion 7a2.
  • a normal vector on the displacement curve F of the cam surface 7b is gradually inclined outward with respect to the axis L0 between the TDC portion 7b2 and the BDC portion 7b1 as the vector position is shifted toward the BDC portion 7b1 from the TDC portion 7b2.
  • the radius of curvature R1 of the second spherical surfaces 8b and 9b of the shoes 8 and 9 is restricted by the radius of curvature of the displacement curve F at the BDC portions 7a1 and 7b1 (indicated by r0 in Fig. 4). If the normal vectors at the BDC portions 7a1 and 7b1 are parallel to the axis L0, therefore, the radius of curvature R1 should be smaller than the radius of curvature r0 of the displacement curve F at the BDC portions 7a1 and 7b1.
  • the radius of curvature R1 can be made greater than the radius of curvature r0.
  • the radius R1 of the BDC portion 7b1 is in fact set larger than the radius of curvature r0 as shown in Fig. 3. Given the above conditions, an arc crossing between the circumferential surface C0 and the second spherical surface 9b and having a radius of curvature "r”, is smaller than the radius R1. As the inclination of the normal vector Vb1 increases, the radius of curvature "r" becomes smaller than the radius R1.
  • the second spherical surface 9b is lifted without contacting the BDC portion 7b1. If the radius of curvature "r" is equal to or smaller than the radius of curvature r0, the second spherical surface 9b comes in line contact with the BDC portion 7b1. By setting the radius of curvature "r” equal to or smaller than the radius of curvature r0 and as close to this radius of curvature r0 as possible, the radius of curvature R1 of the second spherical surface 9b of the shoe 9 becomes greater than the radius of curvature r0. This would reduce the Hertz's pressure occurring between the second spherical surface 9b and the cam surface 7b.
  • the radius of curvature of the second spherical surface 8b of the shoe 8 can also be set greater than the radius of curvature r0, thus reducing the Hertz's pressure between the second spherical surface 8b and the cam surface 7a.
  • the reduction in Hertz's pressure improves the pressure resistance characteristics of the shoes 8 and 9 as well as the wave plate 7. This pressure reduction thus improves the durability of the compressor.
  • the radius of curvature R1 of the second spherical surfaces 8b and 9b can be increased without increasing the diameter of the piston 6 or the diameter of the wave plate 7. It is therefore possible to improve the durability of the compressor without enlarging the compressor.
  • normal vectors Vc1 and Vd1 at BDC portions 7c1 and 7d1 of cam surfaces 7c and 7d may be inclined inward with respect to the axis L0 as shown in Figs. 5 and 6.
  • Normal vectors Vc2 and Vd2 at TDC portions 7c2 and 7d2 of the cam surfaces 7c and 7d are parallel to the axis L0.
  • Fig. 6 illustrates the wave plate 7 turned 90 degrees from the position in Fig. 5.
  • the radius of curvature R1 of the second spherical surfaces 8b and 9b can be set greater than the radius of curvature r0 of the displacement curve F at the BDC portions 7c1 and 7d1.
  • normal vectors Ve1 and Vf1 at BDC portions 7e1 and 7f1 of cam surfaces 7e and 7f may be inclined outward with respect to the axis L0.
  • Normal vectors Ve2 and Vf2 at TDC portions 7e2 and 7f2 may be inclined inward with respect to the axis L0, as shown in Figs. 7 and 8.
  • Fig. 8 illustrates the wave plate 7 turned 90 degrees from the position in Fig. 7.
  • Fig. 10 illustrates the wave plate 7 turned 90 degrees from the position in Fig. 9.
  • both the first surfaces 16a and 16b of shoes 16 and 17, which are to be fitted in a piston, and the second surfaces 16b and 17b of the shoes, which slide on the wave plate 7, may be designed with a cylindrical shape.
  • both the cam surfaces 7i and 7j of the wave plate 7 that lie on a plane containing the axis L0 of the rotary shaft, and the second surfaces 16b and 17b that lie on the same plane have respectively cross sections along a straight line.
  • the first surfaces 16a and 17a slide in contact with the cylindrical inner walls of recesses 6c and 6d of the piston.
  • the shoes 16 and 17 are rotatable within a plane containing the axis L0 of the wave plate 7.
  • the second surfaces 16b and 17b are therefore always in line contact with the cam surfaces 7i and 7j, even if the normal vector Vj at the BDC portion 7j1 is inclined with respect to both the axis L0 of the rotary shaft while the normal vector vi at the TDC portions 7i2 and 7j2 are parallel to the axis L0.
  • the cam surfaces may be formed in a convex shape, and the second surfaces of the shoes, which engage with the cam surfaces, may be formed in a concave shape.
  • a compressor having a plate rotatable about an axis of a rotary shaft and a piston connected to the plate.
  • the plate causes the piston to reciprocate between a top dead center and a bottom dead center in accordance with the rotation movement of the plate.
  • Cam surfaces are provided with the plate for actuating the piston.
  • the cam surfaces have first portions for driving the piston toward the top dead center, and second portions for driving the piston toward the bottom dead center.
  • Transmission members are interposed between the piston and the plate for transmitting the rotation movement of the plate to the piston.
  • the first and second portions cause the transmission members to displace on the cam surfaces.
  • At least one of the first and second portions are arranged to have a normal line extending obliquely to the axis of the rotary shaft for a constant contact between the transmission members and the one of the portions.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
EP94108724A 1993-06-08 1994-06-07 Wave plate type compressor Expired - Lifetime EP0631053B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP5137832A JPH06346840A (ja) 1993-06-08 1993-06-08 ウェーブカム式圧縮機
JP137832/93 1993-06-08

Publications (2)

Publication Number Publication Date
EP0631053A1 EP0631053A1 (en) 1994-12-28
EP0631053B1 true EP0631053B1 (en) 1996-09-18

Family

ID=15207885

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94108724A Expired - Lifetime EP0631053B1 (en) 1993-06-08 1994-06-07 Wave plate type compressor

Country Status (7)

Country Link
US (1) US5477773A (ko)
EP (1) EP0631053B1 (ko)
JP (1) JPH06346840A (ko)
KR (1) KR950001096A (ko)
CA (1) CA2125232A1 (ko)
DE (1) DE69400556T2 (ko)
TW (1) TW273585B (ko)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5638736A (en) * 1994-06-07 1997-06-17 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Wave cam type compressor
JPH08105382A (ja) * 1994-10-05 1996-04-23 Toyota Autom Loom Works Ltd ウエーブカム式圧縮機
JPH094563A (ja) * 1995-04-18 1997-01-07 Zexel Corp 往復式圧縮機
USD384675S (en) * 1995-06-05 1997-10-07 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Wave cam for a compressor
JPH10299656A (ja) * 1997-04-22 1998-11-10 Zexel Corp 往復式圧縮機
DE10124034A1 (de) * 2001-05-16 2002-11-21 Obrist Engineering Gmbh Lusten Hubkolbenmaschine mit einer Gelenkanordnung

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2176300A (en) * 1937-12-06 1939-10-17 Frank J Fette Gas compressor
US2374595A (en) * 1943-09-15 1945-04-24 Western Electric Co Reciprocable telescopic members
JPS57110783A (en) * 1980-12-26 1982-07-09 Nippon Soken Inc Compressor machine
US4640144A (en) * 1985-08-12 1987-02-03 Mclendon Martin Motion interconversion apparatus
JPH0610467B2 (ja) * 1985-11-21 1994-02-09 日本電装株式会社 圧縮機
JPH0610466B2 (ja) * 1985-11-21 1994-02-09 日本電装株式会社 圧縮機
US4756239A (en) * 1986-11-28 1988-07-12 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Anti-rolling structure for double headed piston of disc cam type reciprocative compressor
JPH0794024B2 (ja) * 1986-12-12 1995-10-11 日新製鋼株式会社 撹拌装置付き塗料パン
JPH0444866Y2 (ko) * 1987-03-18 1992-10-22
JPH04179873A (ja) * 1990-11-09 1992-06-26 Toyota Autom Loom Works Ltd 揺動斜板式可変容量圧縮機及び揺動斜板とピストンを係留するシューの加工方法

Also Published As

Publication number Publication date
US5477773A (en) 1995-12-26
DE69400556T2 (de) 1997-03-06
EP0631053A1 (en) 1994-12-28
CA2125232A1 (en) 1994-12-09
JPH06346840A (ja) 1994-12-20
TW273585B (ko) 1996-04-01
DE69400556D1 (de) 1996-10-24
KR950001096A (ko) 1995-01-03

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